Rotary bowling pin distributor with feed controlled chain drive



March 1966 H. M. DOWD ETAL 3,239,221

ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE Filed Aug. 2, 1963 6 Sheets-Sheet l 66 4 HOWARD 79 Y ROYAL L. BARROWS AT TOR N EYS March 8, 1966 DOWD ETAL 3,239,221

ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE 6 Sheets-Sheet 2 Filed Aug. 2, 1965 INVENTORS HOWARD M. DOWD ROYAL. L. BARROWS ATTORN EYS March 8, 1966 H. M. DOWD ETAL ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE 6 Sheets-Sheet 5 Filed Aug. 2. 1963 MQEZTH ATTORN EYS March 8, 1966 v 'H. M. DOWD ETAL 3,239,221

ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE Filed Aug. 2, 1963 6 Sheets-Sheet 4 INVENTO HOWARD M. DOW 5 BY ROYAL L.BARROWS MFM ATTORN EYS March 8, 1966 H. M. DOWD ETAL 3,239,221

ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE Filed Aug. 2, 1963 6 Sheets-Sheet 5 llln i M m X R HOWARD M SWS if BY ROYAL L.B'ARROWS I1 LL Z6; MM

ATTORNEYS March 8, 1966 1-1. M. DOWD ETAL 3,239,221

ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE Filed Aug. 2, 1965 6 Sheets-Sheet 6 HOWARD Q BES V W BY ROYAL 1.. BARRows M AT TOR N EYS minim United States Patent 3,239 221 ROTARY BOWLING PIN DISTRIBUTOR WITH FEED CONTROLLED CHAIN DRIVE Howard M. Dowd, Littleton, and Royal L. Barrows, Middleton, Mass.; W. Leroy Temple, Marlborough, Mass,

and State Street Bank and Trust Company, executors of said Howard M. Dowd, deceased, and said Barrows assignors, by mesne assignments, to Otis Elevator Company, New York, N.Y., a corporation of New York Filed Aug. 2, 1963, Ser. No. 308,609 7 Claims. (Cl. 273-43) This application is a continuation-in-part of our copending prior application Serial No. 22,282, filed April 14, 1960, and now abandoned.

This invention relates to bowling pinsetting machines and more particularly to a new and improved system for 1) retrieving pins and balls from a bowling alley pit, (2) separating the balls and pins, (3) returning the balls to the head of the alley, (4) assembly retrieved pins in groups of ten, and (5) delivering the grouped set of pins to a pinsetting unit.

As is well known, many difierent machines have been designed for picking up bowling pins and balls from an alley pit and returning the balls to the player and resetting the pins on the alley. It is equally well known that these machines all comprise certain functionally equivalent stages or sections, including means for separately removing pins and balls from the alley pit, means for returning balls to the player, means for delivering the removed pins to a storage section, and means for receiving pins from the storage section and respotting them on the alley floor. However, primarily because of a widely held opinion that a single machine cannot be designed to handle more than one size bowling pin or ball, prior bowling pinsetting machines have always been constructed to handle only one specific size or kind or bowling pin. Of particular significance is the fact that most of the different stages of these prior art machines have been so constructed as not be readily adaptable or convertible for handling a second kind of bowling pin. As a consequence, and because of the cost involved, manufacturers of pinsetters have been inclined to concentrate on ten pin or duck pin machines, but not both. Moreover, although rubber duck pins are similar in size and shape to regular duck pins, duck pin machines made heretofore have not been readily adaptable to handle rubber duck pins; and because of the limited number of rubber duck pin alleys in existence, there has been no incentive to make a machine especially for rubber duck pins.

Although there is merit to the opinion that no one machine can handle all kinds of pins or even more than one kind of pin without drastic structural changes, we have observed that it is primarily due to the problems attendant to the pinsetting stages, and also to a lesser extent the pin storage stages. Apart from these two crucial stages, the differences between certain types of pins and balls are not too critical, so that it should be possible to provide separate machines for ten pins, duck pins, and rubber duck pins which are substantially identical in construction except for their pin storage and pinsetting stages and their relatively simple control circuits.

Accordingly, the chief object of the present invention is to provide a novel system for (1) picking up bowling pins and balls from an alley pit, (2) separating the balls and pins, (3) returning the balls to the player end of the alley, and (4) delivering the pins to a pin storage section for ultimate transfer to a pinsetting unit, said system being readily adaptable for handling ten pins, duck pins, or rubber duck pins.

A more specific object of the present invention is to provide a novel pin and ball conveying, separating, and

ice

distributing system which is capable of handling rubber duck pins with as equal ease and efiiciency as regular duck pins and which is readily adaptable to handling ten pins instead of rubber or regular duck pins.

Another object is to provide a new and improved bowling pin and ball elevator.

A further object is to provide a new and improved ball and pin separator.

Still another object is to provide a new and improved control system for a rotary storage unit which indexes one position each time a bowling pin is deposited therein.

Yet another specific object is to provide a novel rotary storage and distributing unit for rubber duck pins and also a novel drive system for the storage unit.

Other objects and many of the attendant advantages of this invention will be readily appreciated as the invention becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

FIG. 1 is a aside elevational view, partly in section, of a pin and ball conveying, separating, and distributing sys tem embodying the present invention;

FIG. 2 is a side elevational view taken from the same standpoint as FIG. 1 but showing only the upper portion of the system with certain parts removed and also showing generally the pin storage and pinsetting stages of a machine;

FIG. 3 is a front elevation of the ball and pin elevator;

FIG. 4 is a plan view based on FIG. 2;

FIG. 5 is a vertical sectional view of the pin storage stage of the machine;

FIG. 6 is a sectional view taken along line 66 of FIG. 5;

FIG. 7 is an enlargement of a portion of FIG. 4;

FIG. 8 is a side elevation, partly in section, of the delivery end of the pin conveyor; and

FIG. 9 is a sectional view taken along line 9-9 of FIG. 7.

The system of the present invention comprises a first conveyor FC (FIG. 1) which lifts both pins P and balls B discharged from a first turntable PT located in an alley pit AP, a second rotating elevated turntable ET which receives pins P from conveyor PC, a ball separator and conveyor BS which functions to separate pins and balls discharged from conveyor FC and to start the balls back toward the head of the alley, and a second conveyor SC which picks up pins from elevated turntable ET and discharges them into a rotatable storage unit SU which indexes one position each time a pin is deposited therein.

First conveyer F C The first conveyor FC may be described as a ball and pin conveyor in contradistinction to conveyor SC which is a pin conveyor only. Conveyor PC includes a pair of parallel vertical side walls or frame members 2 and 4 which are disposed at opposite sides of the rear end of the alley pit AP and are held fixed by suitable supporting cross members such as bars 6 and 8. Side walls 2 and 4 support a vertical partition 10 located rearward of its vertical center line. The bottom edge 12 of partition 10 terminates short of the floor 14 of pit AP, and the top edge 15 (see FIG. 3) is located below the top of side walls 2 and 4.

Side wall 2 supports five inwardly extending rotatable stub shafts 16, 18, 20, 22, and 24 which are provided with sprockets 26, 28, 30, 32 (FIG. 3), and 34 respectively. Mounted on these sprockets is an endless chain 36. A second endless chain 36a (FIG. 3) is mounted on matching sprockets carried by stub shafts mounted on wall 4. For convenience, only certain of the sprockets and stub shafts associated with chain 36:: are shown, and

these are identified by the same numerals as their counterparts associated with chain 36, as, for example, sprocket 32a (FIG. 3).

Chains 36 and 36a are driven through intermediate means from a motor M1 which is mounted on the outside of wall 2. Motor M1 drives a gear reducer unit 40 through a belt 42, and the output shaft of gear reducer unit 40 has a sprocket 44 which drives a chain 46 which rides on an idler sprocket 48 and drives a sprocket 50 mounted on a shaft 52 that is journaled in the top ends of walls 2 and 4. Shaft 52 carries two other sprockets 56 and 58. Sprocket 56 drives a chain 60 that drives a sprocket 62 mounted on shaft 22. The latter drives chain 36 by means of sprocket 32. Sprocket 58 drives a chain 62 that drives a sprocket 64. The latter is mounted on drive shaft 22a which is associated with chain 360:.

Looking now at FIG. 1, chain 36 moves counterclockwise about the circuit established by sprockets 26-34; and commencing at sprocket 26, its path of movement may be described as consisting of (1) a short downward and forward leg, (2) a long upward leg, (3) a short forward and upward leg, (4) a short rearward leg, and a long downward leg.

Chains 36 and 3611 have short, correspondingly located stub shafts 68 and 68a on which are rotatably secured a series of conveying elements 70 of generally arcuate cross section (see FIG. 1). For convenience, conveying elements 70 are referred to hereinafter as scoops. The axis of rotation of each scoop is to one side of its center of gravity so that it will hang vertically as shown in FIG. 1 in the absence of any other supporting force. Each scoop 70 has a bracket 72 at its sides, and each bracket 72 rotatably supports a wheel 74 on the concave side of the conveying element. Side walls 2 and 4 have inwardly extending vertical flanges 76 and 78 adjacent their front edges. Flanges 76 and 78 do not extend down as far as wall instead, their bottom edges abut a curved panel or floor 79 which is attached at its sides to the inner face of walls 2 and 4 and which curves under sprockets 26 and 28. The forward edge of panel 79 is notched as at 81 to facilitate delivery of pins and balls from the pit turntable PT. A heavy, padded movable barrier 83 is hung pivotally over the alley pit. Barrier 83 stops flying pins and balls from slamming into the conveyor section and deflects them down onto the turntable PT.

The alley pit turntable PT is carried by a vertical shaft 82 journaled in a thrust bearing 84. 'Shaft 82 is driven by a chain 86 which in turn is driven by a shaft 88 supported on the outside of wall 2. Shaft 88 carries a pulley 90 which is driven from a motor M2 acting through a chain drive 92, a shaft 94, and a pulley and belt drive 96. Each gutter of the alley may be provided with a gutter belt GB driven by a pulley 100 on a shaft 102. Shaft 102 is driven by shaft 88, acting through a pulley and belt drive 104. The gutter belts move pins from the ends of the gutters onto turntable PT.

It is to be noted that the space between the bottom edge 12 of partition 10 and curved panel 79 is less than the largest diameter of a bowling pin. Consequently, balls and pins deposited by the turntable PT will accumulate in front of partition 10 until picked up by a scoop 70. As each successive scoop 70 is carried downward by chains 36 and 36a, it will be restrained against oscillation by partition 10 acting on wheels 74 or on the trailing edge of the scoop, depending on the direction in which the scoop tends to rotate on shafts 68. In practice, it is preferred that the scoop be mounted so that wheels 74 will ride on the rear surface of partition 10 as shown in FIG. 1. When the wheels pass below partition 10, scoops 70 are free to be pivoted upwardly and forwardly (counte rclockwise in FIG. 1) and will do so upon engagement with curved floor panel 79. Because of the angle of the path followed by the chains in moving from sprocket 0 p cket 28, an the eccentric mounting of the scoops on the stub shafts 68 and 68a, the leading edge of each scoop will remain in contact with floor panel 79 as it moves forward and upward under a pin and/or ball lying on floor panel 79. The curvature of floor panel 79 forces each scoop to assume a horizontal position, and it is retained in that position by flanges 76 and 78 which provide a support for its leading edge as it moves upward. As each scoop reaches the top of flanges 76 and 78, chains 36 and 36a begin moving forward. This produces a lifting force at the rear of the scoop, causing it to tilt clockwise. When this occurs, the balls and/or pins on the conveying element are dumped forward out from between walls 2 and 4 in a trajectory or fall directed at elevated turntable ET. The wheels 74 clear flanges 76 and 78 soon after the scoop is unloaded, thereby allowing the scoop to hang vertically in moving rearward along the horizontal leg extending between sprockets 32 and 34 and then downward behind wall 10.

Turntable ET and conveyor SC Turntable ET is of conical shape ('FIG'. 2) and is mounton a vertical shaft which is journaled in a thrust bearing 112 supported on a fixed horizontal platform 114 lo-' cated above the alley pit. Shaft 110 carries a sprocket 116 which is driven by a chain 118. The latter is driven by a sprocket 120 located on the upper end of shaft 88. Thus, elevated turntable ET is also driven by motor M2.

Surrounding turntable ET is a Curved wall 122 which is supported on legs 124 resting on platform 114. The upper portion of the inner surface of wall 122 is of nonskid character as represented by the stippled area 122a in FIG. 2. Preferably, this is obtained by applying a rub ber covering thereto. This non-skid portion extends down to about 2-2%. inches above the edge of turntable ET. Wall 122 extends above the apex of the concial turntable by a substantial amount, preferably a foot, so that pins cannot bounce over it off of the turntable. At a predetermined location, wall 122 is split to provide a vertical slot or opening 126 which is utilized for removal of pins by conveyor SC. One end 128 of the wall is bent outward on an increasing radius greater than the other end 130 so as to facilitate passage of pins into opening 126. The width of opening 126, i.e., the spacing between the split ends 128 and 130, is greater than the diameter of the head and neck of a bowling pin but smaller than the largest diameter of the body of the same pin. Turntable ET rotates counterclockwise (FIG. 4). Pins on the turntable tend to move outwardly but are retained on the turntable by wall 122 until they approach opening 126 where they are picked up and removed by conveyor SC.

It is necessary that the pins on the rotating turntable be oriented with their heads in leading position. Other-- wise they will not be picked up and removed by conveyor SC. It is to achieve this orientation of the pins that the inner surface of wall 122 is made non-skid. If it were not non-skid, any pins whose heads were in trailing position would tend to remain in that position instead of reversing themselves as required. The function of the non skid surface is easily explained. If the head of a pin is trailing, centrifugal force will throw the body of the pins outward against wall 122. The non-skid surface slows down the pin and causes it to drag. When this occurs, due in part to the round shape of the pin body, the pin will turn around so as to place the head in leading position. With the pin body in trailing position, the pin body apparently exerts more centrifugal force on the wall than does the pin head. Therefore, the pin will resist further rotat1on and the head will remain in leading position. In this position, it is easily directed into the opening 126 wh1ch it will be picked up by one of the pin carriers, of conveyor SC.

Second conveyor SC Conveyor SC comprises a pair of side: frame members: 134 and 136 which are supported by riqtforrr 11A andl which in turn support extensions 138 and 140 which are substantially U-shaped and which terminate over the rotary storage unit SU. These side frame members and their extensions each rotatably support a plurality of stub shafts 142 on which are mounted sprockets 144-. The sprockets on the two side frame members carry separate but identical endless conveyor chains 146 and 146a. The sprockets are positioned so that the chains follow closed paths which approximately parallel the outline or profile of the frame members and their extensions. All but two of the sprockets 144 are mounted on stub shafts 142. These two sprockets (one on each frame member) are not visible in the drawings, but they are mounted on a shaft 150 (FIG. 4) which is journaled in side frame members 134 and 136 at their bottom ends at about the level of platform 114. Chains 146 and 146a are driven by the sprockets secured on shaft 150. Shaft 150 is driven from a motor M3 acting through a belt drive 152, a gear reducer 154, a chain drive 156, and a spring clutch 158. Connected between chains 146 and 146a is a series of pin pickup elements 160. These pickup elements, hereinafter sometimes referred to as pin carriers, are essentially U-shaped yokes, and their ends are rotatably secured to chains 146 and 146a so that they can swivel under the weight of pins picked up from turntable ET. The chains carry pin carriers 160 down along the rear edges and up along the front edges of side frame members 134 and 136. These pin carriers ride up immediately adjacent to opening 126 so that if a pin is sticking out through the opening, it will be caught up by one of the pin carriers and carried by the latter to the forward end of extensions 138 and 140, where it is dropped into rotatable storage unit SU which indexes one position each time a pin is deposited by conveyor SC. Seating of a pin in the index loosens it from its pin carrier which is moved down a little below the neck of the pin before moving up again. While the carrier is loose on the pin, the indexing of the storage unit removes the pin from the yoke and the empty yoke then continues upwardly, rearwardly, downwardly, and upwardly again along the path determined by chains 146 and 146a to pick up another pin from turntable ET. A pair of horizontal plates 161 and 162 (FIG. 4) are attached to frame extensions 13% and 140 to prevent the returning pin carriers from dangling down on their rearward leg of travel.

Ball and pin separator The ball and pin separator BS comprises two rotatable bars 164 and 166 which are located in front of side walls 2 and 4 above elevated turntable ET. Bar 164 is set closer to walls 2 and 4 and lower than bar 166. Bar 164 is journaled at one end in a fixed bearing block 168 secured to side wall 4 and at the other end in a bearing block 1'72 secured to side wall 2. Bar 164 is pitched downward toward bearing 168. Bar 166 is journaled at one end in a bearing block 174 secured to an angular strut 176 which is secured at its ends to wall 41. The other end of bar 166 is rotatably supported by a hearing block 178 mounted on a horizontal arm 130 which is attached at one end to wall 2 and at the other end to an inclined strut 132 which also is secured to wall 2. Bar 166 is slanted at the same angle as bar 164.

Bars 164 and 166 have sprockets 184 and 186 respectively on their higher ends. Both sprockets are driven by a chain 138 which is driven by a sprocket 196 on shaft 22 associated with wall 2.

As viewed in FIG. 4, bars 164 and 166 rotate counterclockwise. In the case of ten pins, the spacing between bars 160 and 162 is less than the diameter of a ten pin bowling ball but greater than the largest diameter of the body of a ten. pin. Similarly, in the case of regular duck pins, the spacing between the bars is less than the diameter of the bowling ball but greater than the largest diameter of the body of a regular duck pin.

However, in the case of a rubber duck pin, the spacing between the two bars is less than the diameter of the ball and less than the outside diameter of the rubberband, but greater than the largest diameter of the wooden pin itself Starting at the lower ends of bars 164 and 166 and curving forward and downward onto a ball return BR (FIG. 4) are two bars 192 and 194. These bars receive balls rolling off of the adjacent ends of bars 164 and 166 and guide them onto ball return BR. Thus bars 164 and 166 intercept balls and pins dumped from conveyor FC and separate them by retaining the balls and allowing the pins to pass through. In the case of ten pins and ordinary duck pins, the difference in. sizes between the balls and pins is sufficiently great to permit the pins to pass readily down between bars 166 and 162 without rotating the latter. However, in the case of rubber duck pins, the diameter of the rubber band (4 inches) is so close in size to the ball diameter (5 inches) that when the bars are spaced to just retain the balls, they will also retain the pins unless the pins are oriented with their axes at an angle to the bars. The bars are rotated so as to make certain that the pins are not hung up on the bars. When the bars are rotated, they exert both a rotative and squeezing effect on the pins. Some of the pins that are hung up are shifted just enough to fall down between the bars onto turntable ET. The pins that do not shift readily are forced down between the bars, their rubber bands being compressed or squeezed sufficiently to permit accomplishment of this mode of operation. Locating the two bars so that one is at a different level than the other magnifies the effect of the bars on the pins and makes it easier to pass the pins while rejecting the balls.

Storage unit S U The storage unit SU illustrated in the drawings is designed to handle rubber duck pins, but it may be replaced by other storage units designed to handle ten pins or regular duck pins.

The storage unit SU (FIGS. 2 and 5) (also sometimes identified as the distributor) comprises a vertical shaft 198 secured to a platform 200, a lower disk 202 attached to a rotatable bearing 264 mounted on shaft 198, an upper annular ring 2116 locked to disk 262 by pins 208, and an intermediate disk 210 which is secured to a rotatable bearing 212 also mounted on shaft 198. Although only one pin 268 is visible in FIG. 5, it is to be understood that a plurality of pins are used to connect ring 206 to disk 202. Pins 20f; are located in a circle slightly larger than disk 2113. A reinforcing ring 214 is secured to the underside of disk 202 and rides on a plurality of wheels 216 secured to platform 26f]. Wheels 216 support the entire assembly for ready rotation on shaft 198. Small rollers 21S positioned in slots in disk 262 support disk 214).

Lower disk 202 has ten equally spaced holes 220 (FIG. 4) which are larger in diameter than the rubber band of a rubber duck pin. Disk 266 has ten holes 222 which are in registration with holes 22%. Holes 222 are as large as or preferably larger than holes 220. Intermediate disk 211) has ten holes 224 whose outline corresponds to that formed by two intersecting circles. Each hole 224 has a smaller portion 224a whose diameter is approximately as large as the largest diameter of the wooden body of a rubber duck pin and smaller than the outside diameter of its rubber band. The diameter of the larger portion 224!) is greater than the outside diameter of the rubber band, and preferably equal to the diameter of holes 220.

In other words, as shown in FIG. 4, intermediate disk 216 is provided with ten sets of holes 224 wherein each set is formed of two interconnecting holes 224a and 22421. In each instance, hole 224]) has a diameter sufficient to permit the passage of a pin whereas hole 224a has a diameter sufficient to pass a portion of a pin but insufiicient to pass the maximum diameter of the pin. The portion where holes 224a and 22% interconnect in each set of holes 224 forms a passage having a width equal to the diameter of the smaller hole 224a.

Intermediate disk 210 carries a bracket 230 (FIG. 4) on its upper surface. Bracket 230 has two upright portions which carry set screws 232, 234 and 236. Pivotally connected to the disk 210 is an arm 238. This arm is held in place by a pivot pin 240. However, it cannot rotate due to set screws 232 and 234 which engage it at opposite sides of the pivot pin 240. These set screws exert equal and opposite forces so as to keep the arm stationary. At one end of arm 238 there is pivotally connected a lever 242. The opposite end of this lever 242 is pivotally connected by a pivot pin 244 to an arm 246 which is attached to the upper end of a shaft 248. Shaft 248 is rotatably supported by a bushing 250 which is mounted in disk 202. Shaft 248 extends through lower disk 202 and is provided at its bottom end with a second arm 252 (FIG. 5). It is to be noted that disk 210 has two large wedge-shaped slots 254 (FIGS. 4 and 7) one of which functions as a large passageway for shaft 248. Arms 242 and 246 form a toggle linkage. Arm 246 is urged toward bracket 230 by a spring 256 which is connected to a bearing 212 to which is secured intermediate disk 210. Arm 242 engages set screw 236, the latter being adjusted so that the knuckle or toggle joint formed at pivot 244 by arms 242 and 246 will be held beyond center position by spring 256, as shown in FIG. 4. The normal position of disk 210 relative to disks 202 and 206 is such that the smaller hole portions 224a are in registration with holes 220 and 222. In this position, a pin deposited head up in a hole 222 will be supported by disk 210 because the rubber band of the pin will overlap a smaller hole portion 224a.

Cooperating with arm 252 (FIG. 5) is a stub shaft 258 mounted on platform 200. A roller 260 is mounted on the upper end of shaft 258. When the disk 202 is turned, the arm 252, at a designated point in its circle of rotation, will engage the roller 260. When this occurs, shaft 248 will be rotated in a direction to shift pivot 244 outward, causing arms 242 and 246 to bend, so as to draw shaft 248 toward arm 238.

In other words, when shaft 248 is rotated by engagement of arm 252 with roller 260, the disk 210 will be caused to rotate relative to disks 202 and 206. Since disk 202 is rotated counterclockwise (as viewed in FIG. 4), disk 210 will have a relative movement clockwise. The movement will be suflicient to shift the large portions 224]; of holes 224 into registration with holes 220 and 222 long enough to free any and all pins which are supported by the disk 210. When arm 252 slips past roller 260, spring 256 will immediately draw arms 242 and 246 back to the position shown in FIG. 4, thereby restoring disk 210 to its normal position relative to disks 202 and 206. This will place the smaller portions 224a back into registration with holes 220 and 222. Thereafter, when additional pins are dropped into the rotary distributor, the rubber bands thereof will set on the portions of disk 210 visible from above through holes 222, as in FIG. 4. These additional pins will be released when the distributor has rotated sufficiently to again move arm 252 past roller 260. Hence, the position of the distributor will be the same for all dumping operations.

When the pins are dumped from the distributor SU, they fall into separate storage and delivery chutes 266 which are aimed to deliver them in a triangular lineup to a vertically reciprocal pinsetter board PS (FIG. 2). However, since they are not to be deposited on the pinsetter board until needed, means are provided for preventing discharge of the pins from chutes 266 until called for (see FIG. 5). These means are generally of the form illustrated and described in our copending application Serial No. 625,739, filed December 3, 1956, and now Patent No. 3,063,716, and comprise transversely extending, horizontal fingers 268 (FIG. 5) which are part of a horizontal rack 270 that is mounted at the bottom ends of the tubes. Rack 270 is reciprocated longitudinally, i.e., parallel to the alley by suitable means (not shown). Rack 270 normally is in position to support pins within tubes 266. When the rack is reciprocated, the fingers move out far enough to release the pins which they support, whereupon they drop onto the pinsetter board PS.

Since the rubber band on a rubber duck pin has a relatively high friction surface, it is not permissible to construct chutes 266 of just any material that comes to mind. Chutes 266 must have certain characteristics in order to be acceptable. They must be slippery, sturdy, easily fabricated, resilient, relatively light weight, long lasting, relatively quiet, and preferably with one or more apertures of sutficient size to inspect for jammed pins. We found that no such material is available, but the same characteristics may be achieved by fashioning the chutes of expanded sheet steel as illustrated at 272 in FIG. 5 and then coating the chutes with tetrafluoroethylene plastic 274 (see FIG. 6). The plastic coating provides a highly slippery surface so that the pins fall easily through and out of the tubes. Our chutes are vastly more quiet than other chutes heretofore used, e.g., chutes made of uncoated sheet metal or fiberboard. The plastic coating stops the chutes from reverberating and also acts as a cushion for the pins so that the wooden bodies thereof do not abrade or wear like they do in chutes made of other materials.

It is to be noted that the direction of movement of pin carriers as they approach the distributor SU is along a straight line running through the center of two consecutive holes 222 in the top disk 206. One of these holes 222a is in a position to receive a pin from conveyor SC, and the other holes 222b immediately precedes hole 222a (counting in the direction of rotation). Thus, rotation of the distributor acts to direct pins deposited therein by conveyor SC along a path substantially straight away from the conveyor. This path facilitates removal of pins P from the pin carriers 160.

Drive system for storage unit SU Rotation of storage unit SU is accomplished by means of a clutch-controlled chain drive system generally identified by numeral 280 which is actuated by pins transported by conveyor SC. The storage unit will index one position each time its chain drive system is actuated by a pin. This chain drive system, including its operating controls, is shown in FIGS. 4, 7, 8 and 9. At this point, it is to be noted that the peripheral edge of disk 202 is provided with ten slots or notches 282 Which are disposed alternately with its holes 220. These slots accommodate upstanding pins 284 carried by an endless chain 236. The chain 286 is mounted on two sprockets 288 and 290 which are attached to upright shafts 292 and 294 rotatably supported on a horizontal platform 296. Shaft 294 also carries a bevel gear 298 which is driven by a bevel gear 300. The latter gear 300 is afiixed to a shaft 302 which is journaled in two plates 304 and 306. Mounted on shaft 302 is a coil spring clutch which consists of a coil spring 308, a driven clutch member 310 having a reduced diameter section (not visible) on which part of spring 308 is wound, and a driving clutch member 312 which also has a reduced diameter section (barely visible in FIG. 9) on which part of spring 308 is wounded. The driving clutch member 312 also carries a sprocket 314. The driven clutch member 310 is keyed to shaft 302, so it can move axially but not circumferentially relative to the shaft. The driving clutch member 312 is rotatable relative to shaft 302. Spacers 316 prevent clutch member 312 from moving axially away from clutch member 310. Another spacer member 318 keyed to shaft 302 acts through bolts 320 screwed therein to keep clutch member 310 from moving away from clutch member 312. Bolts 320 act to keep spacer member 318 and clutch member 310 spaced apart. Bolts 320 permit adjustment of the spacing between the two clutch members so as to keep them in supporting relation with the ends of the spring 308.

Sprocket 314 (FIG. 9) is driven by a chain 324 (FIG. 7) which is driven by a sprocket 326 on the output shaft of a gear reducer 328 that is driven by a pulley and belt drive system 330 from a motor M4. Sprocket 314 is driven continuously by motor M4, and if certain means described hereinafter were not provided, the spring clutch would drive shaft 302 without interruption. In this connection, it is to be noted that sprocket 314 is driven in a direction to compress the spring, and this causes clutch member 310 to be driven by clutch member 312. Preferably, but not necessarily, one end of the spring is fixedly secured to driven clutch member 310. The other end 332 of the spring is bent at right angles so as to extend longitudinally of the spring across a substantial number of turns. If this end of the spring is held against rotation, the spring will tend to unwind and, therefore, it will slip on clutch member 312. When this occurs, shaft 302 will not turn. In practice, spring 308 is permitted to slip a substantial portion of the time, and its ends 332 is released only when it is desired to rotate the distributor or storage unit SU.

The spring 308 (FIG. 9) is held against rotation by a lever 334 (FIG. 7) which is pivotally secured intermediate its ends to a bracket 336 mounted on platform 296. Lever 334 is best to provide a laterally extending stop arm 338 located adjacent to spring 308. The opposite end of lever 334 is urged away from platform 296 by a compression coil spring 340 (FIG. 7). Normally, spring 340 keeps stop arm 338 in position to be engaged by and interfere with rotation of the free end 332 of clutch spring 308. However, if lever 334 is pivoted down in opposition to spring 340, its stop arm 338 will move up out of engagement with the bent end 332 of spring 308, thereby allowing the spring to drive shaft 302. Obviously, if lever 334 is allowed to return to its normal position immediately after spring end 332 is released, the operating period of the clutch will be one revolution. By proper selection of gears 298 and 300, one revolution of shaft 302 is sufficient to advance chain 286 a distance suflicient to index the distributor SU one position, i.e'., the distance between successive holes 222. As chain 286 rotates, its pins 284 mate with slots 282 to drive the distributor. The length of chain 286 and the spacing of pins 284 are such that when the clutch is disengaged, one of the pins (see 284a) will be at sprocket 290 at least partly beyond shaft 294 but still at least partly in one of the slots 282. In this position, the pin 284a will oppose continued rotation of the distributor. Hence, pins 284 not only drive the distributor 'but also act as a brake therefor when the clutch is disengaged.

Movement of lever 334 is effected by a flexible cable 346 (FIG. 8), one end of which comes up through platform 296 inside of coil spring 340 and is tied to the lever at 348 (FIG. 7). The other end of cable 346 is secured to a lever arm 350 which is pivotally mounted on the side frame extension 140 of conveyor SC (FIG. 8). Also mounted on side frame extension 140 is a pillow block 352 which supports one end of a rotatable shaft 356. The other end of shaft 356 is supported by a second pillow block 358 mounted on the opposite side frame extension 138. Shaft 356 carries a depending arm 360 (FIG. 4) having a roller 362 (FIGS. 4 and 8) at its bottom end. Roller 362 extends down for enough to be engaged by each pin carrier 160 on its upper return run over plates 161 and 162. Each time roller 362 is engaged by an empty pin carrier, arm 360 is pivoted counterclockwise (FIG. 8) under the force of the moving pin carrier. Attached to shaft 356 where it projects from pillow block 352 is another arm 364. Pivotally secured to arm 364 is an elongated rod 366 (FIG. 8). The bottom end of 10 rod 366 is threaded to accommodate a flanged nut 368. Rod 366 is slidably supported in a peripheral groove formed in a pulley 370 mounted on a stub shaft 372 a tached to side frame extension 140.

A second rod 374 (FIG. 8) is pivotally secured to arm 350. Rod 374 is also threaded at its free end to accommodate a nut 376 having a flange 377. Rod 374 extends through an enlarged ring 378 attached to side frame extension 140. Ring 378 (FIG. 8) functions to stop rod 374 from pivoting up and down beyond predetermined limits. Normally, rod 374 rests on a pawl 380 that is attached to a horizontal shaft 382 which is journaled in the two side frame extensions 138 and 140 at a level between the upper and lower horizontal runs of chains 146 and 146a. Near its midpoint, shaft 382 (FIG. 8) carries a radial arm 384 which extends down far enough to be struck by the heads of pins conveyed by pin carriers traveling toward rotary storage unit SU. Arm 384 has sufficient weight to overcome the movement of pawl 380; hence, arm 384 normally hangs straight down. To make certain that arm 384 is pivoted by each passing pin, a plate 386 is secured on the underside of plates 161 and 162. Plate 386 is horizontal in cross section. In longitudinal section (FIG. 8), it comprises a declined upstream portion and a horizontal downstream portion. Arm 384 extends down through the horizontal portion of plate 386, the latter having a suitable elongated slot which permits the arm to be swung clockwise (as seen in FIG. 8). When the head of a traveling pin engages the declined upstream portion of plate 386, it is forced downward in opposition to the force exerted by the weight of the body of the pin which is in leading position. This opposing force of the weight of the body keeps the head firm against plate 386 so that it will not oscillate and so that arm 384, and not it, will yield when brought into engagement with each other. Pawl 380 normally occupies the position shown in FIG. 8 so that its tip 388 is below flange 377 and its opposite end is spaced far enough from rod 366 so as not to be engaged by the flange of nut 368 when rod 366 is moved upwardly by pivotal movement of lever 364 due to engagement of roller 362 by a passing pin carrier.

Operation of the above-described drive system for storage unit SU will now be described. Assuming that conveyor SC is operating but that it carries no pins, the bent end 338 of lever 334 (FIG. 7) will keep the spring clutch disengaged and the rotary distributor SU will be stopped with one of the holes 222 located at the discharge end of conveyor SC. This is the position occuped by hole 22211 in FIG. 4. At the same time, pawl 380 will be as shown in FIG. 8. Each time an empty returning pin carrier hits roller 362, rod 366 will move up and then down again relative to pulley 370 without engaging pawl 380. If now a pin is picked up by the conveyor from turntable ET, it will be carried along under plate 386 and will strike arm 384 as it travels. Arm 384 will yield under the force of the moving pin, causing shaft 382 to rotate clockwise (as seen in FIG. 8). Pawl 380 will rotate with shaft 382, and its point 388 will cam flange 377 upward as it rotates. As soon is the pin in question has passed, arm 384 will tend to return to its normal vertical position, but it will not be able to do so because flange 377 will intercept the point 388 of pawl 380. Rod 374 tends to yield to allow pawl 380 to clear flange 377, but it is prevented from doing so because of the resistance oflered by cable 346 under the influence of spring 340. As a result, pawl 380 will remain latched by flange 377. When pawl 380 is so latched, its end opposite point 388 will hang lower than normal in position to be engaged by the flange of nut 368 on rod 366. Thus, the next time that rod 366 is pulled upwardly by counterclockwise movement of arm 364, pawl 380 will be urged counterclockwise by the flange on nut 368. As pawl 380 is turned counterclockwise, its point 388 will act through flange 377 to pivot arm 350 clockwise. This exerts a pull on cable 346 suflicient to pull lever 334 clear of clutch spring 308.

I 1 The clutch will immediately cause shaft 302 to turn, thereby causing the storage unit to urn. As soon as point 388 of pawl 380 clears flange 377, spring 340 will restore lever 334 to its normal postion. This happens sufficiently fast to limit the clutch to one revolution, which is just enough to index storage unit SU one position.

It is to be noted that the pin carriers 160 are equally spaced and that roller 362 is so located that, when a forwardly moving pin carrier 160 is approximately directly below arm 384, it will be approximately half Way between two successive rearwardly moving pin carriers. Thus, although pawl 380 is not latched each time a pin carrier moves below arm 384 (since the pin carrier may be empty), unlatching of pawl 380 will always occur after a predetermined interval determined by the spacing and the speed of the pin carriers. In practice, the timing is such that the pawl is unlatched and the spring clutch is engaged just before the SC driving chains 146 and 146a reach their lowest level and reverse directions at the discharge end of conveyor SC. As seen in FIGS. 2 and 8, the chains move downwardly in passing about sprockets 144a and reverse directions in passing about sprockets 14411. The level of sprockets 144a is such that a pin carried by a pin carrier approaching the sprockets will seat in storage unit SU just after its pin carrier has passed by sprockets 144a and before it reaches sprockets 144b. The pin seats in the storage unit before it begins to turn. Continued downward movement of the pin carrier after its pin has bottomed in the storage unit relaxes the grip of the pin carrier so that the pin will move free of the carrier as the storage unit is rotated. Rotation of the storage unit is sufficiently fast to remove the pin from its carrier before the latter can regrip it after passing about sprockets 1441').

Summary The advantages of the foregoing system and of its several novel sub-assemblies are many. The chief advantage is its universality. Starting with the illustrated embodiment which is especially designed for handling rubber duck pins, it is an easy matter to adapt it for regular duck pins or the larger ten pins. The pit turntable PT and the scoop-type conveyor PC can handle all three types of pins without change. The ball separator can handle both rubber and regular duck pins without change, although it is not necessary that shafts 164 and 166 be rotated for regular duck pins. For ten pins, shafts 164 and 166 would be separated to a greater extent, just enough to pass the ten pins but not the ten pin bowling ball. Turntable ET can be used without change for all three types of pins. Conveyor SC can be used without change for regular duck pins; for ten pins, it is only necessary to widen opening 126 and to replace pin carriers 160 with pin carriers larger in size so as to accommodate the larger ten pins.

Storage unit SU is not suitable for duck pins or ten pins. However, it is easily replaceable by one which is capable of containing regular duck pins or ten pins, e.g., one like the one shown in our aforementioned Patent No. 3,063,716. The drive system for the storage unit and the control system for the spring clutch can be used without any significant changes so long as the storage unit has notches like notches 282. Similarly, storage rack 270 can be used without change for all three types of pins. Chutes 266 may be made large enough to handle all three types of pins. Preferably, however, they are made just large enough to handle both types of duck pins only; for ten pins, it is preferred to use larger diameter chutes. Although not shown, it is contemplated also that the same alley sweeping mechanism may be used for all three types of pins since the only requirement of a sweep mechanism is that it clean the alley of balls and pins.

Therefore, except for the rotary distributor SU, the pinsetter board PS (including means for retrieving standing pins) and any specific control circuits, the illustrated components can be used almost without change to make (1) a machine designed to handle rubber duck pins, (2) a machine designed to handle regular duck pins, or (3) a machine designed to handle ten pins.

Other advantages are obtained by applicants scooptype conveyor PC which can lift both balls and pins. For one thing, the scoops can be made sufficiently wide (as viewed in FIG. 3) so as to pick up more than one ball or pin at a time. This minimizes piling up of pins and balls on pit turntable PT. For another thing, the depth of conveyor PC (as viewed in FIG. 1) can be relatively shallow since the scoops occupy little space when traveling downward behind partition 10. This is especially important where a machine is to be installed in an old alley having limited space for a pinsetter machine.

Another advantage is afforded by bars 164 and 166 which not only separate the balls and pins but also act as an extension of the ball return BR. Bars 164 and 166 eliminate the need for a separate ball elevator running from pit turntable PT to ball return BR. In addition, they do not interfere with the flow of balls and pins out of the alley pit as is usually the case where separation of balls and pins is conducted in the pit. As a result, the balls are returned to the head of the alley in less time than was possible heretofore. This is especially important in the case of ten pins where the bowler uses his own ball and will not throw another.

Still another important advantage is presented by the drive and drive control system for the rotary storage unit. Heretofore it has been the practice to control indexing by means of electrical switches, relays, solenoids, etc. However, servicing electrical circuits is always a problem; and if a breakdown occurs during a busy period, extensive revenue may be lost before repairs can be made by a qualified Serviceman. On the other hand, it has been observed that mechanical failures not only occur with less frequency, but they can be repaired in less time and usually without need for a skilled mechanic. Hence, breakdown time is materially less. Except for motor M4, the storage unit drive and drive control systems disclosed herein are purely mechanical. As such, they are sturdy and dependable, and any trouble which occurs is instantly detectable. Best of all, the timing of the spring clutch cannot be fooled with. Once the machine is assembled, the timing is fixed and correct.

Additional advantages are presented by chutes 266. They are sturdy, will last for the life of the machine, allow inspection of pins therein, produce little noise when struck by dropping pins, cushion the impact of dropping pins whereby to reduce damage to the pins, and offer very little friction so that pins drop into and out of them rapidly and easily.

Obviously, many modifications and variations of the invention are possible in the light of the above teachings. It is to be understood, therefore, that the invention is not limited in its application to the details of construction and arrangement of parts specifically described or illustrated, and that within the scope of the appended claims, it may be practiced otherwise than as specifically described or illustrated.

We claim:

1. In a bowling pinsetting machine having a circular rotary pin distributor mounted in a vertical axis on a base and adapted to receive one by one .the number of bowling pins constituting a set in a like number of bowling pin receiving pockets arranged evenly in circular array thereon;

and bowling pin feed means adapted to deliver bowling .pins sequentially to said distributor;

means for rotating said distributor and for indexing each of said pockets sequentially in bowling pin receiving position adjacent the delivery end of said feed means comprising a plurality of radial slots arranged evenly about a peripheral portion of said distributor;

an endless chain mounted for horizontal travel on a plurality of sprockets supported on said base adjacent said distributor, one run of said chain between adjoining sprockets describing a chord of said distributor;

a plurality of upstanding slot engaging pins mounted on said chain in slot engaging position, successive saidpins adapted to engage successive said slots said slot engaging vpins being so spaced on said chains and the adjoining sprockets supporting the chord describing run of said chain being so located that at least one said pin is in contact with at least one said slot at all time;

and drive means for intermittently driving said chain.

2. A bowling pinsetting machine as claimed in claim 1 wherein one said slot is provided for each said pin receiving pocket.

3. A bowling pinsetting machine as claimed in claim 1 wherein said drive means includes a single revolution clutch, means for driving said clutch, means for releasing said clutch, and gear means connecting said clutch to at least one of said sprockets whereby when said clutch makes one revolution said distributor is advanced a distance equal to the space between adjoining pin-receiving pockets.

4. A bowling pinsetting machine as claimed in claim 3 wherein said pin feed means is provided with a plurality of evenly spaced moving bowling pin carrying means; wherein said clutch release means is associated with said feed means; wherein said clutch release means is provided with a pin contacting means adapted to place said clutch release means in a ready condition upon contact with a bowling pin passing in said feed means; and wherein said clutch release means is provided with a bowling pin carrying means contacting means adapted to release said clutch for a single revolution upon contact with the next succeeding bowling pin carrying means in said feed means to come into contact with said contacting means after said clutch release means is placed in said ready condition.

5. In a bowling pinsetting machine having a circular rotary pin distributor mounted in a vertical axis on a base and adapted to receive one by one the number of noncylindrical bowling pins constituting a set in a like number of bowling pin receiving pockets arranged evenly thereon;

bowling pin feed means adapted to deliver bowling pins sequentially to said distributor;

distributor drive and indexing means adapted to bring the next said pin receiving pocket into .pin receiving position adjacent the delivery end of said feed means as soon as a bowling pin has been delivered to any of said pockets;

and receiving means associated with said base for receiving a set of pins from said distributor;

said rotary distributor including a lower disk and an upper annular ring mounted on said vertical axis in fixed parallel planes and having registering holes of a diameter suflicient to permit passage of axially oriented pins therethrough;

means for retaining pins in said distributor and for releasing pins therefrom into said base associated receiving means when a full set of pins has been received by said distributor com-prising an intermediate disk mounted on said vertical axis and arranged in a plane parallel to and between the planes of said lower disk and said upper ring;

said intermediate disk adapted normally to rotate about said axis in conjunction with said lower disk and said upper annular ring in a first fixed angular relation thereto and optionally to rotate about said axis a minor amount relative to said lower disk and said upper annular ring to a second fixed angular relation relative thereto;

said intermediate disk being provided with two sets of holes, one such set registering with the holes provided in said lower disk and said upper annular ring when said intermediate disk is in said first angular relation and the other such set registering with the holes provided in said lower disk and said upper annular ring when said intermediate disk is in said second angular relation;

the first said set of holes having a diameter suflicient to permit passage of a portion of an axially aligned non-cylindrical bowling pin but insufiicient to pass the maximum diameter of said bowling pin;

the second said set of holes having a diameter sufiicient to permit passage of an axially aligned noncylindrical bowling pin;

a passage connecting each member of the said first set of holes with the corresponding member of said second set of holes;

said passage having a width equal to the diameter of the first said set of holes;

and actuating means associated with said base for rotating said intermediate dis-k relative to said lower disk and said upper annular ring from said first fixed angular relation to said second fixed angular relation;

thereby releasing said pins from said distributor to said receiving means.

6. A bowling pinsetting machine as claimed in claim 5 and especially adapted to be used with rubber duck pins,

wherein the holes in the lower disk, the upper annular ring and in the intermediate disk, \when the latter is in the second angular relation, all have a diameter sufficient to pass the rubber band on said rubber duck pin, and

wherein the holes in the intermediate disk, when the latter is in its first spaced planar relation have a diameter sutficient to pass the largest diameter of the wooden body of such pin but insuificient to pass said rubber band;

whereby said pins are maintained in said distributor in vertical alignment with the lower portion of said rubber bands resting on the upper surface of said intermediate disk adjacent said first said set of holes.

7. A bowling pinsetting machine as claimed in claim 5 wherein said means associated with said base for rotating said intermediate disk comprises a vertical extending crankshaft pivotally mounted on said lower disk,

a laterally extending arm fastened to the upper end of said shaft, said shaft pivotally connected to a second laterally extending shaft pivotally mounted on said intermediate disk and forming together therewith a toggle link,

stop means mounted on said intermediate disk restricting the movement of said toggle link in one direction,

spring means mounted between said intermediate disk and said toggle link normally urging said toggle link against said stop means,

a laterally extending arm fastened to the lower end of said shaft and adapted when carried past a fixed abutting member mounted on said base by the rotation of said distributor to rotate said shaft in a direction to move said toggle link away from said stop means,

and a fixed abutting member mounted on said base in position to intercept said lower arm.

(References on following page) 15 16 References Cited by the Examiner 2,947,541 8/1960 Came et a1. 27343 2,961,237 11/1960 Montooth 275 43 UNITED STATES PATENTS 2,962,284 11/1960 Bilowz 273413 11/192-8 B1shop 273 45 3/1952 pp 27343 5 DELBERT B. LOWE, Primary Examiner, 4/1952 Johns et a1. ANTON O OECHSLE E 9/1958 Montoot'h 612211. 273 43 

1. IN A BOWLING PINSETTING MACHINE HAVING A CIRCULAR ROTARY PIN DISTRIBUTOR MOUNTED IN A VERTICAL AXIS ON A BASE AND ADAPTED TO RECEIVE ONE BY ONE THE NUMBER OF BOWLING PINS CONSTITUTING A SET IN A LIKE NUMBER OF BOWLING PIN RECEIVING POCKETS ARRANGED EVENLY IN CIRCULAR ARRAY THEREON; AND BOWLING PIN FEED MEANS ADAPTED TO DELIVER BOWLING PINS SEQUENTIALLY TO SAID DISTRIBUTOR; MEANS FOR ROTATING SAID DISTRIBUTOR AND FOR INDEXING EACH OF SAID POCKETS SEQUENTIALLY IN BOWLING PIN RECEIVING POSITION ADJACENT THE DELIVERY END OF SAID 